Heat exchangers, condensers and refrigeration equipment

Abstract

The present invention relates to a heat exchanger, a condenser and a refrigeration device, wherein the heat exchanger comprises: a condensing section heat exchange module, the condensing section heat exchange module comprises a first input port and a first output port; a supercooling section heat exchange module, the supercooling section heat exchange module comprises a second input port and a second output port; a connecting pipe, the two ends of the connecting pipe are respectively connected to the first output port and the second input port. The heat exchanger proposed by the present invention is provided with a condensing section heat exchange module and a supercooling section heat exchange module connected in series. After the refrigerant in the condensing section heat exchange module undergoes condensation heat exchange, the liquid refrigerant is collected and flows through the connecting pipe to the supercooling section heat exchange module for secondary cooling. The uniformity of the refrigerant distribution is improved by collecting the liquid refrigerant and redistributing it. On this basis, the supercooling degree of the refrigerant is improved by the secondary cooling of the supercooling section heat exchange module.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration equipment, and in particular to a heat exchanger, a condenser and a refrigeration equipment. Background Art

[0002] This section merely provides background information related to the present disclosure and is not necessarily prior art.

[0003] like Figure 1 As shown, the existing evaporative condensing heat exchanger includes an air inlet pipe 10', a liquid outlet pipe 20' and a heat exchange copper tube 30' arranged side by side between the air inlet pipe and the liquid outlet pipe. A spray device is provided on the top of the evaporative condensing heat exchanger. The spray device sprays water to the heat exchanger, so that the water is sprayed from the top of the heat exchanger to the surface of the heat exchange copper tube 30' with a higher temperature, and the high-temperature gaseous refrigerant in the heat exchange copper tube 30' is mainly cooled by evaporative heat absorption. The refrigerant is gradually condensed into liquid due to heat release during the flow of the heat exchange copper tube, and the evaporated water vapor carried by the fresh air is taken out of the evaporative condensing heat exchanger by the fan.

[0004] Compared with the traditional air-cooled heat exchanger, the heat exchange process of the evaporative condensing heat exchanger has phase change, and the water film temperature on the surface of the heat exchange copper tube is close to the wet bulb temperature of the fresh air, so the condensation effect is better. However, the multiple heat exchange copper tubes 30' in the existing evaporative condensing heat exchanger are connected in parallel in the refrigerant flow path. Since the distances of the multiple heat exchange copper tubes from the refrigerant inlet are different, the resistance of the refrigerant flowing from the refrigerant inlet to each heat exchange copper tube is different, which leads to different refrigerant flow rates of each heat exchange copper tube. Under the same cooling environment, the refrigerant amount and supercooling degree in each heat exchange copper tube are different, resulting in uneven refrigerant distribution and insufficient refrigerant supercooling at the condenser outlet. Summary of the invention

[0005] The purpose of the present invention is to at least solve the problem of insufficient refrigerant supercooling at the condenser outlet caused by uneven refrigerant distribution. This purpose is achieved through the following technical solutions:

[0006] According to the first technical solution of the present invention, a heat exchanger is proposed, comprising: a condensing section heat exchange module, the condensing section heat exchange module comprising a first input port and a first output port; a subcooling section heat exchange module, the subcooling section heat exchange module comprising a second input port and a second output port; a connecting pipe, the two ends of the connecting pipe are respectively connected to the first output port and the second input port.

[0007] According to the heat exchanger proposed in the present invention, a condensation section heat exchange module and a subcooling section heat exchange module are arranged in series. After the refrigerant in the condensation section heat exchange module undergoes condensation heat exchange, the liquid refrigerant is collected and flows through a connecting pipe to the subcooling section heat exchange module for secondary cooling. The uniformity of refrigerant distribution is improved by collecting the liquid refrigerant and then redistributing it. On this basis, the subcooling degree of the refrigerant is improved by utilizing the secondary cooling of the subcooling section heat exchange module.

[0008] In addition, the heat exchanger according to the present invention may also have the following additional technical features:

[0009] In some embodiments of the present invention, the condensing section heat exchange module includes a first input pipe, a first output pipe, and a plurality of first heat exchange pipes connected in parallel between the first input pipe and the first output pipe, the first input port is arranged at the first input pipe, and the first output port is arranged at the first output pipe.

[0010] In some embodiments of the present invention, the subcooling section heat exchange module includes a second input pipe, a second output pipe, and a plurality of second heat exchange pipes connected in parallel between the second input pipe and the second output pipe, the second input port is arranged at the second input pipe, and the second output port is arranged at the second output pipe.

[0011] In some embodiments of the present invention, the inner diameter of the first heat exchange tube is the same as the inner diameter of the second heat exchange tube, and the number of the first heat exchange tubes is greater than the number of the second heat exchange tubes.

[0012] In some embodiments of the present invention, the inner diameter of the first heat exchange tube is greater than the inner diameter of the second heat exchange tube.

[0013] In some embodiments of the present invention, the first input tube and the first output tube are parallel to each other and extend along a first direction; and / or the second input tube and the second output tube are parallel to each other and extend along the first direction.

[0014] In some embodiments of the present invention, the first heat exchange tube includes at least one first bending section, and the second heat exchange tube includes at least one second bending section. Along the first direction, the size of the first bending section is smaller than the size of the second bending section.

[0015] In some embodiments of the present invention, the number of the second bending segments is at least two, and along the first direction, any two adjacent second bending segments are at least partially overlapped.

[0016] In some embodiments of the present invention, the first input pipe is arranged farther away from the second input pipe than the first heat exchange pipe and the first output pipe; and / or the second input pipe is arranged closer to the first output pipe than the second heat exchange pipe and the second output pipe.

[0017] According to the second technical solution of the present invention, a condenser is also proposed, which includes: the heat exchanger described in the first technical solution; a spray water circulation system, the spray water circulation system includes a spray head arranged above the heat exchanger, and the spray head is used to spray water onto the heat exchanger.

[0018] In some embodiments of the present invention, an airflow driving device is further included, and the airflow driving device is used to drive the airflow to flow through the heat exchanger from bottom to top.

[0019] According to the third technical solution of the present invention, a refrigeration device is also provided, and the refrigeration device includes the condenser described in the second technical solution. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Various other advantages and benefits will become apparent to those of ordinary skill in the art by reading the detailed description of the preferred embodiments below. The accompanying drawings are only for the purpose of illustrating the preferred embodiments and are not to be considered as limiting the present invention. Moreover, the same reference numerals are used throughout the accompanying drawings to represent the same components. In the accompanying drawings:

[0021] Figure 1 The schematic diagram of the structure of the evaporative condensing heat exchanger in the prior art is shown schematically;

[0022] Figure 2 The schematic diagram of the structure of the condenser according to the embodiment of the present invention is shown in front view;

[0023] Figure 3 The schematic diagram of the structure of the second heat exchange tube according to the embodiment of the present invention is shown;

[0024] Figure 4 A schematic diagram of a partial structure of a first heat exchange tube according to an embodiment of the present invention is schematically shown;

[0025] Figure 5 The structure diagram of the condenser from the left side according to the embodiment of the present invention is schematically shown;

[0026] Figure 6 The schematic diagram of the structure of the condenser from a top view according to an embodiment of the present invention is shown;

[0027] Figure 7 The structure diagram of the condenser from a rear view perspective according to an embodiment of the present invention is schematically shown;

[0028] Figure 8 The schematic diagram of the structure of the spray pipe and the spray head according to the embodiment of the present invention is schematically shown.

[0029] The reference numerals are as follows:

[0030] 10', air inlet pipe; 20', liquid outlet pipe; 30', heat exchange copper pipe;

[0031] 100. Heat exchanger;

[0032] 10. condensing section heat exchange module; 11. first input pipe; 12. first output pipe; 13. first heat exchange pipe; 131. first bending section;

[0033] 20. Subcooling section heat exchange module; 21. Second input pipe; 22. Second output pipe; 23. Second heat exchange pipe; 231. Second bending section;

[0034] 30. Connecting pipe;

[0035] 200, condenser;

[0036] 201. support frame; 202. spray water circulation system; 2021. spray head; 2022. spray pipe. DETAILED DESCRIPTION

[0037] The exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. Although the exemplary embodiments of the present disclosure are shown in the accompanying drawings, it should be understood that the present disclosure can be implemented in various forms and should not be limited by the embodiments described herein. On the contrary, these embodiments are provided in order to enable a more thorough understanding of the present disclosure and to fully convey the scope of the present disclosure to those skilled in the art.

[0038] It should be understood that the terms used herein are only for the purpose of describing specific example embodiments and are not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms "one", "an" and "said" as used herein may also be meant to include plural forms. The terms "include", "comprise", "contain", and "have" are inclusive, and therefore specify the existence of stated features, steps, operations, elements and / or parts, but do not exclude the existence or addition of one or more other features, steps, operations, elements, parts, and / or combinations thereof. The method steps, processes, and operations described herein are not interpreted as necessarily requiring them to be performed in the specific order described or illustrated, unless the execution order is clearly indicated. It should also be understood that additional or alternative steps may be used.

[0039] Although the terms first, second, third, etc. can be used in the text to describe multiple elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. These terms can only be used to distinguish an element, component, region, layer or section from another region, layer or section. Unless the context clearly indicates, terms such as "first", "second" and other numerical terms do not imply order or sequence when used in the text. Therefore, the first element, component, region, layer or section discussed below can be referred to as the second element, component, region, layer or section without departing from the teaching of the example embodiments.

[0040] For ease of description, spatial relative terms may be used herein to describe the relationship of one element or feature relative to another element or feature as shown in the figure, such as "inside", "outside", "inner side", "outer side", "below", "below", "above", "above", etc. Such spatial relative terms are intended to include different orientations of the device in use or operation in addition to the orientation depicted in the figure. For example, if the device in the figure is turned over, then the elements described as "below other elements or features" or "below other elements or features" will subsequently be oriented as "above other elements or features" or "above other elements or features". Therefore, the example term "below..." can include both upper and lower orientations. The device can be oriented otherwise (rotated 90 degrees or in other directions) and the spatial relative descriptors used in the text are interpreted accordingly.

[0041] In order to solve the technical problem of insufficient refrigerant subcooling at the condenser outlet caused by uneven refrigerant distribution, the present application proposes a heat exchanger, which comprises a condensing section heat exchange module and a subcooling section heat exchange module connected in series. After condensation and heat exchange, the refrigerant in the condensing section heat exchange module is collected in liquid form and flows through a connecting pipe to the subcooling section heat exchange module for secondary cooling. The uniformity of refrigerant distribution is improved by collecting the liquid refrigerant and redistributing it. On this basis, the subcooling of the refrigerant is improved by utilizing the secondary cooling of the subcooling section heat exchange module.

[0042] In some embodiments of the present invention, a heat exchanger is provided, such as Figure 2 As shown, the heat exchanger 100 is an evaporative condensing heat exchanger 100 , and the heat exchanger 100 includes a condensing section heat exchange module 10 , a subcooling section heat exchange module 20 and a connecting pipe 30 .

[0043] The condensing section heat exchange module 10 includes a first input port and a first output port (not shown in the figure), and the subcooling section heat exchange module 20 includes a second input port and a second output port (not shown in the figure). The condensing section heat exchange module 10 and the subcooling section heat exchange module 20 are connected in series in the refrigerant flow path through a connecting pipe 30.

[0044] Specifically, the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 both include heat exchange tubes for the flow of refrigerant, and the heat exchange tubes are made of metal materials with good thermal conductivity, such as copper tubes. The heat exchanger 100 uses water and air as cooling media. When working, the cooling water is pumped to the upper spray head by a water pump, and the cooling water is sprayed on the outer surface of the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 to form a water film. The high-temperature vapor refrigerant enters from the first input port of the condensing section heat exchange module 10, and is absorbed by the cooling water to condense and liquefy and then flows out from the first output port. The two ends of the connecting pipe 30 are respectively connected to the first output port and the second input port. After the refrigerant flows out from the first output port, it is mixed through the connecting pipe 30 and then distributed to the subcooling section heat exchange module 20 more evenly from the second input port. The liquid refrigerant is further cooled in the subcooling section heat exchange module 20 after secondary cooling to obtain a better degree of subcooling. Part of the water that absorbs heat evaporates, and the rest falls into the water collecting tray. The airflow driving device drives the air to pass over the condensation section heat exchange module 10 and the supercooling section heat exchange module 20 to promote the evaporation of the water film, strengthen the condensation heat release, and make the water droplets after absorbing heat be cooled by the air in the process of falling. The evaporated water vapor is discharged by the airflow driving device along with the air, and the water droplets that are not evaporated fall back into the water tray, realizing the recycling of the spray water.

[0045] It should be emphasized that, due to the difference in the amount of refrigerant and its subcooling degree in each heat exchange copper tube of the existing heat exchanger 100, the liquid refrigerant flowing out of the outlet of the heat exchanger 100 has differences in temperature, with some areas being lower and some areas being higher. Some refrigerant with higher temperature may be gasified due to a sudden decrease in pressure after being discharged from the condenser 200, resulting in flash gas phenomenon, thereby further losing subcooling degree. In the present application, the liquid refrigerant discharged from each heat exchange tube in the condensing section heat exchange module 10 is collected in the connecting pipe 30 for mixing, and then flows into the subcooling section heat exchange module 20 again. On the one hand, the uniformity of the distribution of the liquid refrigerant is improved. On the other hand, the refrigerant is cooled again by the subcooling section heat exchange module 20, so that the refrigerant obtains a higher degree of subcooling, which can effectively avoid the flash gas phenomenon and reduce the loss of cooling capacity.

[0046] In some embodiments of the present invention, Figure 2As shown, the condensing section heat exchange module 10 includes a first input pipe 11, a first output pipe 12 and a plurality of first heat exchange pipes 13. The plurality of first heat exchange pipes 13 are arranged side by side between the first input pipe 11 and the first output pipe 12, and the two ends of each first heat exchange pipe 13 are respectively connected to the first input pipe 11 and the first output pipe 12. A first input port is arranged on the first input pipe 11, and a first output port is arranged on the first output pipe 12. The high-temperature gaseous refrigerant flows into the first input pipe 11 from the first input port and is distributed and flows into each first heat exchange pipe 13. The high-temperature gaseous refrigerant in each first heat exchange pipe 13 is absorbed by the cooling water to be condensed and liquefied and then collected in the first output pipe 12, and then flows into the subcooling section heat exchange module 20 through the first output port and the connecting pipe 30.

[0047] The subcooling section heat exchange module 20 includes a second input pipe 21, a second output pipe 22 and a plurality of second heat exchange pipes 23. The plurality of second heat exchange pipes 23 are arranged side by side between the second input pipe 21 and the second output pipe 22, and the two ends of each second heat exchange pipe 23 are respectively connected to the second input pipe 21 and the second output pipe 22. A second input port is arranged on the second input pipe 21, and a second output port is arranged on the second output pipe 22. The liquid refrigerant in the connecting pipe 30 flows into the second input pipe 21 from the second input port, and is distributed to each second heat exchange pipe 23 more evenly through the second input pipe 21. The liquid refrigerant in each second heat exchange pipe 23 is further cooled by the cooling water absorbing heat, so that the refrigerant temperature is further reduced to obtain a better degree of subcooling. After being mixed in the second output pipe 22, it flows out from the second output port.

[0048] It should be noted that, in the present embodiment, by providing the first output pipe 12, the liquid refrigerant with temperature differences flowing out from each first heat exchange tube 13 is first aggregated and mixed in the first output pipe 12, thereby improving the uniformity of the liquid refrigerant to a certain extent. After the first aggregation, the liquid refrigerant passes through the connecting pipe 30, such as the second input pipe 21, and then flows into each second heat exchange tube 23 through a secondary distribution. After the second cooling to obtain a better supercooling degree, it is aggregated to the second output pipe 22 for a second time. On the premise of improving the supercooling degree of the liquid refrigerant, the uniformity of the refrigerant is further improved through the secondary aggregation and mixing.

[0049] In the present embodiment, the first input pipe 11, the first output pipe 12, the second input pipe 21 and the second output pipe 22 are all provided with through holes arranged in sequence, so that the first input pipe 11, the first output pipe 12, the second input pipe 21 and the second output pipe 22 are all in a flute shape, and the first heat exchange pipe 13 and the second heat exchange pipe 23 are inserted into the through holes one by one, so that the first heat exchange pipe 13 is respectively connected with the first input pipe 11 and the first output pipe 12, and the second heat exchange pipe 23 is respectively connected with the second input pipe 21 and the second output pipe 22.

[0050] In some embodiments of the present invention, Figure 2 As shown, the first input pipe 11 and the first output pipe 12 are parallel to each other, the first heat exchange pipe 13 is located between the first input pipe 11 and the first output pipe 12, and the first heat exchange pipe 13 is arranged at a preset angle with the first input pipe 11 and the first output pipe 12. The first input pipe 11 and the first output pipe 12 extend along a first direction, and the first heat exchange pipe 13 is arranged along a second direction.

[0051] In some exemplary embodiments, the first direction is a horizontal direction, and the second direction is perpendicular to the first direction, that is, the preset angle is 90°. In detail, the first input pipe 11 and the first output pipe 12 are arranged in the horizontal direction, and the first heat exchange pipe 13 is arranged in the vertical direction. It should be noted that the first heat exchange pipe 13 is arranged in the vertical direction, which is conducive to increasing the flow speed of the refrigerant in the first heat exchange pipe 13, and increasing the probability of the refrigerant in the first heat exchange pipe 13 generating turbulence, thereby reducing the probability of the refrigerant in the first heat exchange pipe 13 generating laminar flow, so as to improve the heat exchange efficiency between the refrigerant in the first heat exchange pipe 13 and the cooling water through the pipe wall of the first heat exchange pipe 13.

[0052] In other embodiments, the first input pipe 11 and the first output pipe 12 are arranged at an angle to the horizontal direction, and the first heat exchange pipe 13 may also be arranged inclined relative to the first input pipe 11 and the first output pipe 12 .

[0053] In some embodiments of the present invention, Figure 2 As shown, the second input pipe 21 and the second output pipe 22 are parallel to each other, the second heat exchange pipe 23 is located between the second input pipe 21 and the second output pipe 22, and the second heat exchange pipe 23 is arranged at a preset angle with the second input pipe 21 and the second output pipe 22. The second input pipe 21 and the second output pipe 22 extend along the second direction, and the second heat exchange pipe 23 is arranged along the second direction.

[0054] In some exemplary embodiments, Figure 2 As shown, the second direction is the horizontal direction, and the second direction is perpendicular to the second direction, that is, the preset angle is 90°. In detail, the second input pipe 21 and the second output pipe 22 are arranged in the horizontal direction, and the second heat exchange pipe 23 is arranged in the vertical direction. It should be noted that the second heat exchange pipe 23 is arranged in the vertical direction, which is conducive to increasing the flow speed of the refrigerant in the second heat exchange pipe 23, and increasing the probability of the refrigerant in the second heat exchange pipe 23 generating turbulence, thereby reducing the probability of the refrigerant in the second heat exchange pipe 23 generating laminar flow, so as to improve the heat exchange efficiency between the refrigerant in the second heat exchange pipe 23 and the cooling water through the tube wall of the second heat exchange pipe 23.

[0055] In other embodiments, the second input pipe 21 and the second output pipe 22 are arranged at an angle to the horizontal direction, and the second heat exchange pipe 23 may also be arranged tilted relative to the second input pipe 21 and the second output pipe 22 .

[0056] In a specific embodiment, the first input pipe 11 and the first output pipe 12 are parallel to each other and arranged in the horizontal direction, the first heat exchange pipe 13 is arranged in the vertical direction, and the second input pipe 21 and the second output pipe 22 are parallel to each other and arranged in the horizontal direction, the extension direction (i.e., the second direction) of the second heat exchange pipe 23 is arranged in the vertical direction, the first input pipe 11, the first heat exchange pipe 13, and the first output pipe 12 are arranged in sequence from top to bottom, and the second input pipe 21, the second heat exchange pipe 23, and the second output pipe 22 are arranged in sequence from top to bottom. And the subcooling section heat exchange module 20 is arranged below the condensing section heat exchange module 10, so that the high-temperature refrigerant flows from top to bottom and is cooled by the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 in sequence, so that the condensed and liquefied refrigerant naturally flows downward under the action of gravity and separates from the gaseous refrigerant, realizing gas-liquid separation, and preventing the gaseous refrigerant and the liquid refrigerant from mixing and flowing out of the heat exchanger 100.

[0057] In this embodiment, the first input port is located in the middle position of the length direction of the first input pipe 11, and the first output port is located in the middle position of the length direction of the first output pipe 12, which is beneficial for the high-pressure gaseous refrigerant flowing in from the first input port to be more evenly distributed to each first heat exchange tube 13, thereby improving the uniformity of refrigerant distribution and improving the heat exchange efficiency between the refrigerant and cooling water.

[0058] The second input port is located in the middle position of the length direction of the second input pipe 21, and the second output port is located in the middle position of the length direction of the second output pipe 22, which is beneficial for the liquid refrigerant flowing in from the second input port to be more evenly distributed to each second heat exchange tube 23, thereby improving the uniformity of the refrigerant distribution and further improving the supercooling of the refrigerant.

[0059] It should also be noted that there is a phase change in the heat exchange process of the existing evaporative condensing heat exchanger 100, and the water film temperature on the surface of the heat exchange tube is close to the wet bulb temperature of the fresh air, which has a strong condensation effect. Therefore, the existing heat exchanger 100 has the problem of premature condensation and liquefaction of the gas refrigerant in the heat exchange tube, causing a large amount of liquid refrigerant to be filled in the heat exchange tube, which greatly reduces the area of ​​the heat exchange tube where the gas refrigerant is condensing and heat exchanging. When the amount of gas refrigerant added remains unchanged, the area of ​​the condensation heat exchange is reduced, which makes the condensation temperature of the heat exchanger 100 higher. Moreover, liquid refrigerant has a greater flow resistance than gaseous refrigerant in the heat exchange tube. Therefore, the flow rate of the liquid refrigerant in the heat exchange tube is low, which easily causes the liquid refrigerant in the heat exchange tube to have laminar flow, reducing the heat exchange efficiency between the refrigerant passing through the tube wall of the heat exchange tube and the cooling water. In addition, the arrangement of multiple heat exchange tubes in parallel makes the length of the heat exchange tube shorter, and the flow of the refrigerant in the heat exchange tube is shorter, so that the refrigerant cannot be fully cooled and is discharged from the heat exchanger 100, making the supercooling effect of the refrigerant poor. To solve the above problems, the present invention also proposes the following technical solutions.

[0060] In some embodiments, the number of the first heat exchange tubes 13 of the condensing section heat exchange module 10 is different from the number of the second heat exchange tubes 23 of the supercooling section heat exchange module 20. Specifically, the inner diameter of the first heat exchange tube 13 is the same as the inner diameter of the second heat exchange tube 23, and the number of the first heat exchange tubes 13 is greater than the number of the second heat exchange tubes 23. Even if all the first heat exchange tubes 13 of the condensing section heat exchange module 10 have a larger volume, under the condition that the supply amount of the gaseous refrigerant remains unchanged, the condensed and liquefied refrigerant can only fill a smaller area at the bottom of the first heat exchange tube 13, so that the larger area near the top of the first heat exchange tube 13 is in a state of being filled with gaseous refrigerant, thereby increasing the area of ​​condensation heat exchange in the first heat exchange tube 13. Under the condition that the amount of gaseous refrigerant replenishment remains unchanged, the larger area of ​​condensation heat exchange makes the condensation temperature of the refrigerant in the first heat exchange tube 13 lower, so as to achieve a better condensation effect.

[0061] It should also be emphasized that the number of second heat exchange tubes 23 in the subcooling section heat exchange module 20 is relatively small. The smaller number of second heat exchange tubes 23 makes the pipe flow cross-sectional area of ​​all second heat exchange tubes 23 in the subcooling section heat exchange module 20 smaller than the pipe flow cross-sectional area of ​​all first heat exchange tubes 13. Since the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 are both connected in series in the refrigerant flow path, the refrigerant flow rate of the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 is the same. Therefore, the liquid refrigerant in the second heat exchange tube 23 has a higher flow rate. The higher flow rate of the liquid refrigerant increases the probability of turbulence of the refrigerant in the second heat exchange tube 23 and reduces the probability of laminar flow of the refrigerant in the second heat exchange tube 23, so as to improve the heat exchange efficiency between the refrigerant in the second heat exchange tube 23 through the tube wall of the second heat exchange tube 23 and the cooling water, so that the refrigerant obtains sufficient supercooling.

[0062] In this embodiment, the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 is in the range of 1.5 to 5, for example, the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 is 2; or the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 is 2.5; or the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 is 3; or the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 is 3.5; or the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 is 4. It is understandable that the ratio of the number of the first heat exchange tubes 13 to the number of the second heat exchange tubes 23 can also be set to other values, which are not limited here one by one.

[0063] In some embodiments, the inner diameter of the first heat exchange tube 13 of the condensing section heat exchange module 10 is different from the inner diameter of the second heat exchange tube 23 of the supercooling section heat exchange module 20. Specifically, the inner diameter of the first heat exchange tube 13 is larger than the inner diameter of the second heat exchange tube 23, so that all the first heat exchange tubes 13 of the condensing section heat exchange module 10 have a larger volume. When the supply amount of the gaseous refrigerant remains unchanged, the condensed and liquefied refrigerant can only fill a smaller area at the bottom of the first heat exchange tube 13, so that the larger area near the top of the first heat exchange tube 13 is filled with gaseous refrigerant, which increases the area of ​​condensation heat exchange in the first heat exchange tube 13. When the amount of gaseous refrigerant replenishment remains unchanged, the larger area of ​​condensation heat exchange makes the condensation temperature of the refrigerant in the first heat exchange tube 13 lower, so as to achieve a better condensation effect.

[0064] It should also be emphasized that the inner diameter of the second heat exchange tube 23 in the subcooling section heat exchange module 20 is relatively small, so that the pipe flow cross-sectional area of ​​all the second heat exchange tubes 23 of the subcooling section heat exchange module 20 is smaller than the pipe flow cross-sectional area of ​​all the first heat exchange tubes 13. Since the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 are both connected in series in the refrigerant flow path, the refrigerant flow rate of the condensing section heat exchange module 10 and the subcooling section heat exchange module 20 is the same. Therefore, the liquid refrigerant in the second heat exchange tube 23 has a higher flow rate. The higher flow rate of the liquid refrigerant increases the probability of turbulence of the refrigerant in the second heat exchange tube 23 and reduces the probability of laminar flow of the refrigerant in the second heat exchange tube 23, so as to improve the heat exchange efficiency between the refrigerant in the second heat exchange tube 23 through the tube wall of the second heat exchange tube 23 and the cooling water, so that the refrigerant obtains sufficient subcooling.

[0065] In this embodiment, the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 is in the range of 1.5 to 5. For example, the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 is 2; or the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 is 2.5; or the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 is 3; or the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 is 3.5; or the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 is 4. It is understandable that the ratio of the inner diameter of the first heat exchange tube 13 to the inner diameter of the second heat exchange tube 23 can also be set to other values, which are not limited here one by one.

[0066] In some exemplary embodiments, Figure 3 and Figure 4As shown, the first heat exchange tube 13 includes a first bending section 131 or the first heat exchange tube 13 includes a plurality of first bending sections 131 connected end to end, the second heat exchange tube 23 includes a second bending section 231 or the second heat exchange tube 23 includes a plurality of second bending sections 231 connected end to end, and along the first direction, the size L1 of the first bending section 131 is smaller than the size L2 of the second bending section. In this embodiment, the purpose of the size L1 of the first bending section 131 being smaller than the size L2 of the second bending section is that when the number of the second heat exchange tubes 23 is less than that of the first heat exchange tubes 13, the second bending section 231 can enable the second heat exchange tubes 23 to fully occupy the space in the horizontal direction (i.e., the first direction), and increase the total size of the second heat exchange tubes 23, thereby improving the space utilization rate of the subcooling section heat exchange module 20, and improving the heat exchange efficiency of the subcooling section heat exchange module 20, so as to facilitate the refrigerant to obtain a better degree of subcooling.

[0067] In some embodiments, the second heat exchange tube 23 includes two second bending sections 231, or the second heat exchange tube 23 includes multiple second bending sections 231, and each second bending section 231 is connected end to end from top to bottom. In this embodiment, the projections of any two adjacent second bending sections 231 along the first direction at least partially overlap, and when the first direction is horizontal, at least part of the area of ​​any two adjacent second bending sections 231 is at the same horizontal height, and the parts of the two adjacent second bending sections 231 at the same height are arranged at intervals along the first direction, so that the second heat exchange tube 23 can fully occupy the space in the horizontal direction, and increase the total length of the second heat exchange tube 23 in the height space between the second input tube 21 and the second output tube 22, thereby improving the space utilization rate of the subcooling section heat exchange module 20, and improving the heat exchange efficiency of the subcooling section heat exchange module 20, so as to facilitate the refrigerant to obtain a better degree of subcooling.

[0068] According to a second aspect of the present invention, Figure 1 and Figures 5 to 7 As shown, a condenser 200 is also proposed, and the condenser 200 includes: a support frame 201, a heat exchanger 100 and a spray water circulation system 202.

[0069] In detail, the spray water circulation system 202 includes: a spray pipe 2022, a plurality of spray heads 2021, an evaporative water circulation pipeline, a water pump and a water receiving tray (not shown in the figure). The condensing section heat exchange module 10 and the subcooling section heat exchange module 20 are both installed on the support frame 201. Figure 8As shown, a plurality of spray heads 2021 are arranged on the spray pipe 2022 at intervals in sequence. The spray pipe 2022 is fixed on the support frame 201 and is located at the top of the heat exchanger 100. The water receiving tray is arranged at the bottom of the heat exchanger 100. The evaporative water circulation pipeline is connected to the water receiving tray. The water pump is used to drive the water in the water receiving tray to be sprayed onto the surface of the heat exchanger 100 through the evaporative water circulation pipeline through the spray head and form a water film on the surface of the heat exchanger 100. The water film evaporates after absorbing the heat of the heat exchanger 100, thereby reducing the temperature of the refrigerant in the heat exchanger 100 and realizing the heat exchange between the refrigerant circulation system and the spray water circulation system. The unevaporated water of the heat exchanger 100 falls downward into the water receiving tray to realize the circulation of water. In this embodiment, the evaporative water circulation pipeline adopts high-quality plastic pipes, which have high corrosion resistance and long service life. The refrigerant circulation pipeline (such as the first heat exchange tube 13, the second heat exchange tube 23, etc.) is filled with a new environmentally friendly refrigerant R410A, which has high refrigeration efficiency, does not contain chlorine, will not damage the ozone layer, and can effectively reduce carbon dioxide emissions.

[0070] In an exemplary embodiment, the condenser 200 further includes an airflow driving device (not shown in the figure), which can be arranged at the top of the heat exchanger 100 or at the bottom of the heat exchanger 100. The airflow driving device is used to drive the air flow so that the outside air flows through the heat exchanger 100 from bottom to top, so as to force the air to flow through the surface of the heat exchanger 100, promote the evaporation of the water film, and take away the evaporated water vapor, thereby improving the heat exchange efficiency. The panel of the airflow driving device in this embodiment can be painted with heavy anti-corrosion thickened paint and fixed with stainless steel fasteners to ensure the long-term stable operation of the fan.

[0071] Specifically, the spray head includes a plurality of nozzles arranged toward the condensing heat exchanger 100. When the condenser 200 is working, the water in the water receiving tray is pumped to the upper nozzle by the water pump and sprayed on the outer surface of the condensing heat exchanger 100 to form a water film. The high-temperature vapor refrigerant enters the heat exchanger 100, and flows out from the bottom after absorbing heat by the water film. A part of the water that absorbs heat evaporates, and the unevaporated part of the water falls into the water receiving tray. The airflow driving device drives the air to pass over the condensing heat exchanger 100 to promote the evaporation of the water film, strengthen the condensation and heat release of the high-temperature gaseous refrigerant in the heat exchanger 100, and make the water droplets after absorbing heat be cooled by the air in the process of falling. The evaporated water vapor is discharged by the airflow driving device along with the air, and the unevaporated water droplets fall back into the water tray. Compared with ordinary air-cooled units, the evaporative condensing heat exchanger 100 has a higher heat exchange efficiency.

[0072] According to a third aspect of the present invention, a refrigeration device is further provided, comprising a condenser 200. The refrigeration device may be a central air conditioner, and the condenser 200 provides cooling to the heat exchanger 100 in the indoor unit of the central air conditioner, thereby adjusting the air temperature of the indoor space.

[0073] In other embodiments, the refrigeration equipment may also be an air temperature regulating device for supplying cold to a cold storage, or an ice maker for making ice cubes, etc., which are not limited here one by one.

[0074] The above is only a preferred specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed by the present invention should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims

1. A heat exchanger, characterized in that: include: A condensing section heat exchange module, wherein the condensing section heat exchange module comprises a first input port and a first output port; A subcooling section heat exchange module, wherein the subcooling section heat exchange module comprises a second input port and a second output port; A connecting pipe, two ends of which are respectively connected to the first output port and the second input port; The condensing section heat exchange module comprises a first input pipe, a first output pipe and a plurality of first heat exchange pipes connected in parallel between the first input pipe and the first output pipe, the first input port is provided at the first input pipe, and the first output port is provided at the first output pipe; The subcooling section heat exchange module includes a second input pipe, a second output pipe, and a plurality of second heat exchange pipes connected in parallel between the second input pipe and the second output pipe, the second input port is provided at the second input pipe, and the second output port is provided at the second output pipe; The first input pipe and the first output pipe are parallel to each other and arranged in the horizontal direction, the first heat exchange pipe is arranged in the vertical direction, and the second input pipe and the second output pipe are parallel to each other and arranged in the horizontal direction, the second heat exchange pipe is arranged in the vertical direction, the first input pipe, the first heat exchange pipe, and the first output pipe are arranged in sequence from top to bottom, and the second input pipe, the second heat exchange pipe, and the second output pipe are arranged in sequence from top to bottom.

2. The heat exchanger according to claim 1, characterized in that: The inner diameter of the first heat exchange tube is the same as the inner diameter of the second heat exchange tube, and the number of the first heat exchange tubes is greater than the number of the second heat exchange tubes.

3. The heat exchanger according to claim 1, characterized in that: The inner diameter of the first heat exchange tube is greater than the inner diameter of the second heat exchange tube.

4. The heat exchanger according to any one of claims 1 to 3, characterized in that: The first heat exchange tube includes at least one first bending section, and the second heat exchange tube includes at least one second bending section. Along the first direction, the size of the first bending section is smaller than the size of the second bending section.

5. The heat exchanger according to claim 4, characterized in that: The number of the second bending segments is at least two, and along the first direction, any two adjacent second bending segments are at least partially overlapped.

6. The heat exchanger according to any one of claims 1 to 3, characterized in that: The first input pipe is arranged farther away from the second input pipe than the first heat exchange pipe and the first output pipe; and / or The second input pipe is disposed closer to the first output pipe than the second heat exchange pipe and the second output pipe.

7. A condenser, characterized in that: The condenser comprises: The heat exchanger according to any one of claims 1 to 6; A spray water circulation system, wherein the spray water circulation system comprises a spray head arranged above the heat exchanger, and the spray head is used for spraying water to the heat exchanger.

8. The condenser according to claim 7, characterized in that It also includes an airflow driving device, which is used to drive the airflow to flow through the heat exchanger from bottom to top.

9. A refrigeration device, characterized in that: The refrigeration device comprises the condenser according to claim 7 or 8.

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